DE102006042078A1 - clutch - Google Patents

Abstract

The present invention relates to a coupling having an input-side terminal for a drive motor and an output-side terminal for an output shaft and arranged therebetween disk set, which is brought via a piston-cylinder unit in the state of friction. It is essential to act on the disk set via two additively complementary piston-cylinder units.

Description

The The present invention relates to a coupling according to the preamble of Main claim.

such Coupling is well known.

Usually such a coupling is located between a drive motor, e.g. an internal combustion engine and an output whose rotational movement over the Coupling coupled with the rotary motion of the drive motor or should be decoupled from it or, if the clutch plates in the steady state of the sliding friction, to only a part to transmit the drive-side torque to the output side.

at Such a clutch, for example, the output side as Shaft formed, preferably as a hollow shaft, while the drive side with the coupling housing rotatably connected.

Between Drive side and output side is the disk set, wherein the number of slats used in each case to be transmitted Torques and the thermal performance of the clutch influenced.

Higher torques also require a higher one Number of slats.

For the respective ones clutch states (open, closed, synchronization or trolling) must be a controllable Contact pressure allows be, with which the disk pack according to the Basic Law of Gleitreibungszustandes dependent from the respective acting contact pressure only none, the maximum or part of the maximum Torque transfers.

Furthermore there are also use cases, e.g. in the range of marine couplings, in which the speed a propeller must be slower than the least possible of the machine conditional speed.

This Operating condition occurs e.g. on when the ship's position is kept on approach should be, and therefore the speed of the propeller regardless of The speed of the motor must be adjustable.

This Requirement can be though over conventional Clutches with the intended use in the naval sector certainly accomplish However, it is an object of the invention, the effort to control reduce such couplings.

These Task solves the invention with the features of the main claim.

Out The invention has the advantage that virtually no change the size of such Clutches higher Torque transferable are.

Especially for the Purpose as a ship clutch it is recommended that the trolling condition over a To realize control loop, preferably at a higher pressure level in the pressure chamber of the second piston-cylinder unit on the preferably smaller piston area acts.

The invention is based on the following:
In principle, each clutch is loaded by two different operating states.

in the first operating state, the clutch is engaged, i. the rotational movement of the drive machine is slip-free on the rotational movement transmitted to the output shaft.

at a marine coupling corresponds to this operating condition e.g. one Drive from Hamburg to New York.

Of the other operating condition is given when the marine coupling with must work in order to prevent slippage, e.g. the position of the To hold the ship.

in the first operating state therefore requires high contact forces to to operate the plate pack slip-free.

in the second operating state requires a sensitive control behavior, which must take place at a contact pressure, in which the clutch is in slipping operation.

The is characterized according to the invention realized that the second piston-cylinder unit on the one hand on smaller pressurized surfaces feature can, on the other hand be subjected to a higher pressure.

The higher Pressure level can be naturally finer settle while the smaller effective area the piston-cylinder unit the pressure in the Slip operation despite the higher pending pressure levels are limited.

It is therefore also a feature of the invention that the clutch in the slip mode from a preferably smaller sized second piston-cylinder unit is applied while the clutch in the engagement mode, So with a rigid connection between drive and output, through the adding contact forces of both Piston-cylinder units is acted upon.

Independently of However, the clutch in rigidly engaged operation alone from a correspondingly large-sized first piston-cylinder unit are applied, if due the involved printing surfaces the for the stiction necessary contact pressure even from a lower pressure level can be realized.

Of the However, the essential aspect of the invention is the possible advantage the slip-free clutch operation by acting on both piston-cylinder units to be able to realize.

This Advantage is achieved in that the contact pressure on the disk pack works, taking into account the areas involved additive from the contact pressure the first piston-cylinder unit plus the contact pressure of the second piston-cylinder unit yields.

The Contact forces of both Piston-cylinder units are added using the invention.

The Consequently, the force acting on the disk pack is eliminated consideration the geometric relationships additive from the summation of the two individual forces, the each result from the individual piston-cylinder units.

In order to However, with the same size of the coupling, the transferable Torque also increased accordingly.

The from the available standing pressure level overall achievable contact pressure of the disk set increases accordingly and in conjunction with the smaller piston area of the second Piston-cylinder unit, in particular for the stated purposes The clutch in the maritime area also better regulated at unconfirmed first Piston-cylinder unit.

Essential for the Invention is therefore the arrangement of two piston-cylinder units, each communicating with a pressure source, each of which is in engaging direction acts on the disk pack.

Either Both piston-cylinder units are powered by a single pressure source supplied or each one of its own.

On This way, the contact pressure of both piston-cylinder units can be additively superimposed on the disk set, without the size of such Clutches must increase.

The Power density of the coupling, as a parameter in the form of the quotient of transferable power in relation to to the volume of construction increases.

Of the completeness it should be mentioned, that also the additive arrangement of more than two piston-cylinder units of the Invention can be included.

In In this case, the statements made above apply accordingly.

there can both piston-cylinder units over have separate pressure sources.

Both Piston-cylinder units can but also be connected to the same pressure source.

Want you about it In addition, especially for the Trolling operation in the maritime sector have a wear-free coupling offers It is important to run the disk pack in an oil bath.

It is therefore a suitable for the maritime sector Development of the invention, in which deliberately to achieve a below the minimum speed of the machine lying speed of the propeller arranged between the drive motor and output shaft coupling is driven in grinding mode.

there will the for the standstill in the current required speed of the propeller on the contact pressure of the Disc set by means of only one of the two piston-cylinder units, preferably because of the better control behavior of the smaller piston-cylinder unit.

Become the pistons of both piston-cylinder units are connected to one another in such a way that that with displacement of only one piston of the piston of the other Piston-cylinder unit is forcibly coupled mitverlagert is by simultaneous filling both pressure chambers Immediately the additive contact force from both piston-cylinder units without delay exerted on the disk set, while the filling only the smaller piston-cylinder unit improved Grinding operation possible.

The Connection can over it Be also so designed that both pistons in the direction of disengagement in principle only simultaneously and in the same direction are displaced.

In the release direction have to the two pistons then likewise, as well as in the Einrückrichtung, be rigidly coupled with each other.

This let yourself in exemplary embodiments realize a simple Axialverschraubung.

The invention has also recognized that both piston-cylinder units within the same Clutch housing can sit.

The Overall size of a Such a coupling is therefore the size of a clutch with only a single piston-cylinder unit does not exceed.

at This development of the invention will therefore anyway within the clutch housing for disposal standing space through the installation of the second piston-cylinder unit, and possibly other piston-cylinder units, better utilized to in this way the contact pressure to increase the disc pack.

in the In principle, the invention is therefore a parallel circuit two piston-cylinder units in the sense that to generate the contact pressure with pressure oil acted upon piston surfaces complement each other additively, the smaller piston area but the second piston-cylinder unit also acted alone is.

to Achieving small sizes about that also proposed, the two piston-cylinder units axially to arrange one after the other, d. h., that both piston-cylinder units are on the same side of the disk pack can sit and act together with their pistons on the pressure ring, with which the contact pressure is applied to the disk pack.

there can both piston-cylinder units together over the usually in the hollow shaft provided pressure oil passage with pressure oil be supplied.

To this purpose are for both piston-cylinder units each communicating with the pressure chamber radial channels provided, if necessary, from one and the same source of pressurized oil can be fed.

These Development of the invention requires the least amount of construction, because only the already existing components within the meaning of the invention added Need to become.

there can be the second piston-cylinder unit, the same as the first Piston-cylinder unit has an effective in the direction of engagement of the clutch piston surface, definitely have a smaller size.

Then could the piston surface of the piston of the second piston-cylinder unit within the lie the piston of the first piston-cylinder unit spanned piston surface around the housing diameter to keep the clutch small.

By simple axial offset of the two piston surfaces can therefore be within the same coupling housing readily accommodate the two piston-cylinder units.

advantageous constructive features see above out for both piston-cylinder units each one on the inner driver firmly anchored support flange before, on which the respective cylinder is axially rigid with the coupling shaft connected is.

Furthermore can the support flange the second piston-cylinder unit, which is structurally conditioned between the first and the second Piston-cylinder unit is also used as a support surface for those force transmitters, the for the disengagement movement responsible for the clutch are.

For this will be embodiments specified.

in the Below, the invention will be discussed in more detail with reference to embodiments.

It demonstrate:

1 the coupling according to the invention in axial section;

2 Detail view of the two piston-cylinder units;

3 Detail view of the lubricating oil supply of the disk pack.

Provided not otherwise stated below, the following description applies always for all figures.

The figures show a coupling 1 ,

The coupling 1 is provided with an input-side terminal for a drive motor and with an output-side terminal for an output shaft.

Inlet check Connection and output terminal are not differentiated here in detail.

Usually one of the two connections is with the coupling housing 3 and the other with the inner driver 2 connected.

Between the clutch housing 3 and the inner driver 2 in the present case are the individual lamellae of the disk pack 4 arranged, of which every second lamella with an external toothing in a corresponding internal toothing of the coupling housing 3 and each one derige lamella with an internal toothing on an external toothing of the inner cam 2 sitting.

The slat package 4 will be in the direction of engagement 5 acted upon with pressure, so that between the respective adjacent lamellae of the disk set a circumferentially acting resulting frictional force arises whose size is dependent on the respective coefficient of friction of adjacent fins and in the direction of engagement 5 acting axial force.

In the release direction 6 is a separately acting force transmitter 12 provided to open the disk pack.

In the direction of engagement acts a piston-cylinder unit 7 , Which can be acted upon by a channel system with pressurized fluid.

In the present case, the channel system consists for example of an axial channel 17 in the interior driver 2 is introduced and hereof outgoing radial channels 18 in the pressure room 9 this piston-cylinder unit 7 lead, which is also referred to as the "first" piston-cylinder unit.

The radial canal 18 thus flows into the first pressure chamber 9 , and acts on the piston surface 10 of the piston 8th the piston-cylinder unit 7 in the Einrückrichtung 5 ,

This will cause the piston 8th the piston-cylinder unit 7 towards the slat package 4 shifted until the slat set 4 facing abutment surface 25 of the piston 8th to the opposite outer surface of the disk pack 4 encounters.

Thereafter, with further pressure build-up, the disk pack is more and more compressed and the required torque-transmitting frictional force between the input side and output side of the clutch 1 built up.

It is essential now that in addition to this first piston-cylinder unit 7 a second piston-cylinder unit 13 is provided.

The further piston-cylinder unit 13 also has a piston 14 on, but the second pressure chamber 15 closes and when filled with a suitable pressurized fluid the piston 14 also in the direction of the disk pack 4 to relocate is able.

For this purpose, the second pressure chamber 15 also communicatively connected via a channel system with a pressure source.

Here, in a first embodiment, the channel system consists of a in the hollow shaft 2 introduced axial channel 17 from which a radial channel 18a ultimately, with the second pressure chamber 15 communicated.

This means that the radial outer end of the radial channel 18a via a suitable channel system directly to the second pressure chamber 15 connected is.

Alternatively, the radial channel 18a for filling the second piston-cylinder unit 13 serves, via its own axial channel 17a with the pressure source 11 . 11a communicate. It can be an own pressure source 11a act, preferably at a higher pressure level than the pressure source 11 the first piston-cylinder unit 7 ,

It is understandable that when filling the first piston-cylinder unit 7 the associated piston 8th towards the slat package 4 is relocated. However, this applies in the same way when the piston surface is acted upon 16 of the piston 14 the second piston-cylinder unit 13 , so in the end, the end face 25 with sufficient displacement to the left in the direction of the disk pack 4 in front of the associated mating surface of the outermost lam abuts and compressed in this way with further pressure build-up, the entire lamella packet accordingly.

As the present coupling 1 is particularly suitable for operation in the abrasive state, it is additionally provided that the disk pack 4 running in an oil bath.

For this purpose are in the axial longitudinal region of the disk set 4 some more radial channels 26a -G, which also has one in the rotary driver 2 introduced axial channel 17 be supplied with lubricating oil.

The lubricating oil passes through the radial channels in this way 26a -G in that area of the coupling 1 , where the individual slats of the disk pack to be lubricated 4 to sit.

How to continue 1 It can be seen that the pistons are 8th and 14 the two piston-cylinder units 7 and 13 so interconnected that when shifting only a single of the two pistons 8th or 14 the other piston 14 or 8th in the Einrückrichtung 5 is relocated.

In the present case, the two pistons 8th and 14 over the coupling screw 27 clamped together so that both pistons 8th and 14 so to speak as a unit are synchronously movable.

The movement of the two pistons 8th and 14 is therefore always the same direction and synchronous, so that already with small amounts of pressurized fluid in just one or even in both pressure chambers, the entire unit of the two piston-cylinder units in the direction of the disk set 4 is relocated.

In addition, by the coupling screw 27 also achieved that both pistons 8th and 14 also in the release direction 6 synchronous and simultaneously and rectified are movable.

Of particular advantage, however, is the embodiment shown, in which both piston-cylinder units 7 and 13 within the same coupling housing 3 to sit.

On This is the way it is the available standing space of the clutch housing optimally utilized and the power density of the coupling without changing the external dimensions increased in the context of the invention.

Due to the arrangement of the two piston-cylinder units 7 and 13 in the axial direction one behind the other, the outer diameter of conventional clutch housing 3 just be taken over.

Although the piston-cylinder units are then ring-shaped, but this corresponds well with the prior art, in addition, the advantage of a relatively low pressure levels is to mention, which nevertheless due to the additively complementary pressure surfaces of the piston 8th and 14 leads to a correspondingly higher contact pressure.

Nevertheless is the control behavior in the grinding operation due to the smaller area the second piston-cylinder unit improved.

Both piston-cylinder units can work accordingly 1 be connected to one or with each separate pressure sources.

There It also follows that the two piston surfaces of the first and second Piston-cylinder unit can be essentially the same size proposed to both piston-cylinder units each to connect to a single pressure source.

Each piston-cylinder unit consists of one fixed to the inner driver 2 connected, for example, connected by suitable screw, component and a movable thereto in the axial direction component.

To support the piston-cylinder units 7 and 13 on the inner driver 2 here serve support flanges 19 and 22 which are immovable in both axial directions on the inner driver 2 to sit.

In particular, the support flange 19 can be rigid with the Innenmitnehmer via a screw connection 2 be connected.

The shown embodiment differs from this solution variant.

In the case of the right support flange 19 is a seagull for this purpose 20 in a corresponding circumferential groove of the inner driver 2 used.

This would be the support flange 19 in the direction of the disk pack 4 be secured against slipping away.

Around the support flange 19 Also to hold in the opposite direction is a clamping ring 21 provided on the other side of the Seegerings 20 attacks and against the support flange 19 is screwed.

The second support flange 22 is towards the slat package 4 against a diameter step in the Innenmitnehmer 2 supported and, in particular, how 3 shows, opposite the Innenmitnehmer 2 screwed.

The second support flange forms in the direction of the disk pack 4 extending extension, which is tightly guided on its outer periphery in the front area.

The sealing zone is here from the inner periphery of a rigid with the second piston 14 connected and in the direction of the disk pack 4 wegerstreckenden ring formed, so that the piston 14 the second piston-cylinder unit 13 practically on the outer diameter of the support flange 22 is guided sealing, with the clamping screws 23 , preferably at the periphery of the support flange 22 sit distributed, so to speak with respect to the Innenmitnehmers 2 fixed component of the second piston-cylinder unit 13 fix.

In addition, it can be seen that in the support flange 22 the second piston-cylinder unit 13 Guide holes distributed around the circumference 24 are introduced in the axial direction, so that at this axially non-displaceable part of the second piston-cylinder unit 13 the force transmitter 12 attached, with the help of which the piston 8th the first piston-cylinder unit 7 in the direction of release 6 is moved as soon as the pressurization decreases.

About the axial coupling of the two pistons 8th and 14 by means of the coupling screw 27 This is also the piston 14 the second piston-cylinder unit 13 at the same time and rectified with the piston 8th the first piston-cylinder unit 7 in the direction of release 6 relocated.

1

clutch

2

inner drive

3

clutch housing

4

disk pack

5

engaging direction

6

disengaging

7

first Piston-cylinder unit

8th

Piston of 7

9

first pressure chamber

10

Piston surface in the direction 5

11

pressure source

11a

pressure source

12

force transmitter

13

second Piston-cylinder unit

14

Piston of 13

15

second pressure chamber

16

Piston surface in the direction 5

17

axial

17a

axial

18

radial channel

18a

radial channel

19

first support flange

20

circlip

21

clamping ring

22

second support flange

23

clamping screw

24

guide bore

25

face

26a-g

radial channel

27

coupling screw

M

actuator

GPS

Global Positioning system

Claims (17)

Clutch ( 1 ) with an input-side connection ( 2 ; 3 ) for a drive motor and an output-side connection ( 3 ; 2 ) for an output shaft and arranged therebetween disk set ( 4 ), which in Einrückrichtung ( 5 ) through the piston ( 8th ) a piston-cylinder unit ( 7 ) via a channel system ( 17 . 18 ) can be acted upon by pressure fluid and with a in the release direction ( 6 ) on the piston ( 8th ) of the piston-cylinder unit ( 7 ) acting force transmitter ( 12 ) and with the following features: - it is a second piston-cylinder unit ( 13 ), - the piston of which ( 14 ) has another in Einrückrichtung ( 5 ) of the coupling ( 1 ) acted upon with pressurized fluid second piston surface ( 16 ), - the second piston surface ( 16 ) closes another second pressure chamber ( 15 ), - the second pressure chamber ( 15 ) communicates via a second channel system ( 17 . 18a ; 17a . 18a ) with a pressure source ( 11 ; 11a ). Clutch ( 1 ) according to claim 1, characterized in that the disk pack ( 4 ) in an oil bath. Clutch ( 1 ) according to claim 1 or 2, characterized in that the pistons ( 8th . 14 ) of both piston-cylinder units ( 7 . 13 ) are so interconnected ( 27 ) are that the piston ( 14 ) of the second piston-cylinder unit ( 13 ) of the piston ( 8th ) of the first piston-cylinder unit ( 7 ) at least in the direction of engagement ( 5 ) is mitverlagert. Clutch ( 1 ) according to claim 3, characterized in that the pistons ( 8th . 14 ) of both piston-cylinder units ( 7 . 13 ) are so interconnected ( 27 ) are that the piston ( 14 ) of the second piston-cylinder unit ( 13 ) of the piston ( 8th ) of the first piston-cylinder unit ( 7 ) also in the release direction ( 6 ) is mitverlagert. Clutch ( 1 ) according to one of claims 1 to 4, characterized in that both piston-cylinder units ( 7 . 13 ) within the same coupling housing ( 3 ) to sit. Clutch ( 1 ) according to claim 5, characterized in that both piston-cylinder units ( 7 . 13 ) are arranged axially one behind the other. Clutch ( 1 ) according to claim 5 or 6, characterized in that both piston-cylinder units ( 7 . 13 ) annularly on an inner driver ( 2 ) and that the inner driver ( 2 ) a pressure oil channel ( 17 ), from which both piston-cylinder units ( 7 . 13 ) via respective radial channels ( 18 . 18a ) are pressurized with pressurized oil. Clutch ( 1 ) according to claim 5 or 6, characterized in that the inner driver ( 2 ) for each piston-cylinder unit ( 7 . 13 ) each have a separate pressure oil channel ( 17 . 17a ) of which in each case one of the two piston-cylinder units ( 7 . 13 ) via respective radial channels ( 18 . 18a ) is pressurized with pressure oil. Clutch ( 1 ) according to claim 7 or 8, characterized in that both piston-cylinder units ( 7 . 13 ) with the same pressure source ( 11 ) communicate. Clutch ( 1 ) according to claim 8, characterized in that for each piston-cylinder unit ( 7 . 13 ) another pressure source ( 11 . 11a ) is provided. Clutch ( 1 ) according to claim 10, characterized in that the pressure source ( 11a ) of the second piston-cylinder unit ( 7 . 13 ) has a higher pressure level than the pressure source ( 11 ) of the first piston-cylinder unit. Clutch ( 1 ) according to one of claims 5 to 11, characterized in that the piston surface ( 16 ) of the piston ( 14 ) of the second piston-cylinder unit ( 13 ) smaller than that of the piston ( 8th ) of the first piston-cylinder unit ( 7 ) surface ( 10 ). Clutch ( 1 ) according to claim 12, characterized in that both piston-cylinder units ( 7 . 13 ) of one each on the inner driver ( 2 ) fixed in both axial directions ( 5 . 6 ) anchored support flange ( 19 . 22 ) be completed. Clutch ( 1 ) according to claim 13, characterized in that the supporting flange ( 22 ) of the second piston-cylinder unit ( 13 ) between the piston ( 8th ) of the first piston-cylinder unit ( 7 ) and the piston ( 14 ) of the second piston-cylinder unit ( 13 ) is arranged and that between the disk pack ( 4 ) facing away from this support flange ( 22 ) and the disc pack ( 4 ) facing side of the first piston-cylinder unit ( 7 ) in the release direction ( 6 ) of the coupling ( 1 ) acting force transmitter ( 12 ). Clutch ( 1 ) according to claim 14, characterized in that the force transmitter ( 12 ) of over the circumference of the support flange ( 22 ) of the second piston-cylinder unit ( 13 ) distributed compression springs are formed. Clutch ( 1 ) according to claim 15, characterized in that the compression springs in guide bores ( 24 ) of the support flange ( 22 ) of the second piston-cylinder unit ( 13 ) or on the disc pack ( 4 ) facing side of the piston ( 8th ) of the first piston-cylinder unit ( 7 ) to sit. Clutch ( 1 ) according to one of claims 1 to 16, characterized in that the second piston-cylinder unit ( 13 ) is incorporated in a control loop, wherein the pressurizing pressure is a function of an actuator (M) whose setting position is variable in response to deviations from a predetermined global vehicle target position.